Prescision hoe opener with swing link between cylinder and shank

ABSTRACT

A precision hoe opener assembly is provided with improved accuracy of seeding as well as improved control over the opener and packer wheel assemblies. The opener assembly includes a hydraulically-driven parallel linkage assembly, a lost motion linkage, a hoe opener, and a packer wheel. The design provides improved seeding accuracy, by adjusting assembly components to and compensating for changes in terrain elevation.

RELATED APPLICATION

This application is a divisional of U.S. patent application Ser. No.12/141,891, entitled “Precision Hoe Opener Assembly with Swing LinkBetween Cylinder and Shank,” filed Jun. 18, 2008 now U.S. Pat. No.7,866,410, which is hereby incorporated by reference in its entirety,which benefits from the priority of U.S. Provisional Patent ApplicationNo. 60/944,790, entitled “Precision Hoe Opener Assembly with Swing Linkand Biasing Member,” filed Jun. 18, 2007, which is hereby incorporatedby reference in its entirety.

BACKGROUND

The invention relates to agricultural seeders, such as hoe openers andseeding tools used in farming operations to distribute seeds into thesoil.

Generally, precision hoe openers are mounted to the frame of animplement which is towed behind a tractor. These openers may include aground engaging tool that opens the soil, providing a path for seeddeposition into the soil. After the seed is deposited, the groundengaging tool may be followed by a packer wheel that packs the soil ontop of the deposited seed. The packer wheel may be rigidly mountedbehind the ground engaging tool via a structural member or rear frame.Thus, the ground engaging tool and packer wheel generally move togetherwith the same upward and downward motion. This vertical motion, somewhatindependent of the implement frame, allows for more precise placement ofseed in the soil.

Unfortunately, existing precision hoe openers do not adequately addressthe need for height variation over terrain during seeding, or fortransportation when not seeding. It is generally undesirable to pull thehoe opener through soil when merely transporting the opener from onelocation to another. In addition, during seeding, existing openers donot provide adequate vertical motion of the opener and related assemblywithout compromising the load on the ground engaging tool and packerwheel. As a result, variations in the terrain can result in drasticchanges in the packing force of the packer wheel on the terrain beingseeded by the opener and, also, the draft force of the terrain on theground engaging tool. In turn, this variation in ground opening forceand packing force can result in non-uniform seeding depths and packingdensity in the terrain being seeded.

The distance between the packer wheel and ground engaging tool can alsoaffect the seeding accuracy of the opener apparatus. Existing precisionhoe openers have a fixed distance between the packer wheel and groundengaging tool. A greater distance between the components will causevariations in the terrain to affect the force on the opener or packerwheel to an even greater degree. This will also result in non-uniformforce applied to the soil by the two components, which reduces seedingaccuracy.

Existing precision hoe openers also require substantial force to raisethe opener assembly, including the ground engaging assembly and packerwheel. This requirement results in the use of large hydraulic cylindersto raise the apparatus, due to the overall length and weight of eachopener assembly. This hydraulic equipment is costly and is demanding ofresources (i.e., hydraulic power) from other portions of the tractor andseeding implement.

There is a need, therefore, for improved arrangements in precision hoeopeners that improve the accuracy of the seeding operation. There is aparticular need for a precision hoe opener configuration that appliesforces to the ground engaging tool and the packing wheel to improveseeding depth and accuracy.

BRIEF DESCRIPTION

It should be understood that the following discussion, and specificembodiments, are presented merely to provide the reader with a briefsummary of certain forms the invention might take and that theseembodiments are not intended to limit the scope of the invention.Indeed, the invention may encompass a variety of aspects that may not beset forth below.

Embodiments of the present invention address the problem of inadequatevertical motion of the tool by optimizing the geometric relationship ofthe cylinder, parallel linkage, ground engaging tool, and packer wheel.Specifically, embodiments of the present invention allow for additionalmotion between the shank and cylinder by incorporating a swing linkassembly between these elements. The swing link enables the cylinder totravel farther than if it were rigidly mounted to the shank, providingfor alternative positions as the cylinder is extended or retracted.These alternative positions allow for both additional vertical motion ofthe assembly and the desired loading on the opener and packer wheel.

Embodiments of the present invention include draft compensation in theparallel linkage to counteract draft forces placed on the groundengaging tool during operation. One of the difficulties is that at anypoint where the linkage is not parallel with the ground, force at thepacker wheel will fluctuate as the draft force applied to the groundengaging tool varies. Embodiments of the present invention areconfigured to enable the hydraulic load of the cylinder to compensateand counteract the varying draft loads on the opener, therebymaintaining a substantially constant packing pressure on the packerwheel.

Various refinements exist of the features noted above in relation to thevarious aspects of the present invention. Further features may also beincorporated in these various aspects as well. These refinements andadditional features may exist individually or in any combination. Forinstance, various features discussed below in relation to one or more ofthe illustrated embodiments may be incorporated into any of theabove-described aspects of the present invention alone or in anycombination. Again, the brief summary presented above is intended onlyto familiarize the reader with certain aspects and contexts of thepresent invention without limitation to subject matter set forth inclaims.

DRAWINGS

These and other features, aspects, and advantages of the presentinvention will become better understood when the following detaileddescription is read with reference to the accompanying drawings in whichlike characters represent like parts throughout the drawings, wherein:

FIG. 1 is a perspective view of an embodiment of a precision hoe openerhaving a frame support, a cylinder, a swing link assembly, a rear frameassembly, a ground engaging tool, and a packer wheel;

FIG. 2 is a side view of an embodiment of the precision hoe opener ofFIG. 1;

FIG. 3 is a sectional view of an embodiment of the opener assembly ofFIGS. 1 and 2, wherein the packer wheel, the rear frame assembly, andcertain elements are removed to enhance clarity;

FIG. 4 is a perspective view of an embodiment of the shank mountadapter, the swing link assembly, and associated features shown FIG. 3;

FIG. 5 is a side elevational view of an embodiment of the precision hoeopener as illustrated in FIG. 1, further illustrating a neutral orhorizontal operating position to illustrate draft compensation when theassembly is in this operating position;

FIG. 6 is a side elevational view of an embodiment of the precision hoeopener as illustrated in FIG. 1, further illustrating a second operatingposition with the draft compensation loading provided by the cylinder tothe packer wheel when the assembly is in this operating position;

FIG. 7 is a side elevational view of an embodiment of the precision hoeopener as illustrated in FIG. 1, further illustrating a third operatingposition to illustrate the draft compensation loading provided by thecylinder to the packer wheel when the assembly is in this operatingposition;

FIG. 8 is a perspective view of an entire precision hoe drill assemblysystem, including multiple opener assemblies and the implement framethat they are attached thereto;

FIG. 9 is a perspective view of another embodiment of a precision hoeopener having a frame support, a cylinder, a swing link assembly, a rearframe assembly, a ground engaging tool, and a packer wheel;

FIG. 10 is a side view of an embodiment of the precision hoe opener ofFIG. 9; and

FIG. 11 is an exploded perspective view of an embodiment of theprecision hoe opener shown in FIG. 9.

DETAILED DESCRIPTION

Turning now to the drawings and referring first to FIG. 1, an embodimentof a precision hoe opener assembly is illustrated and designatedgenerally by reference numeral 10. Precision opener assembly 10 includesa frame support 12, an actuator or drive such as a cylinder 14 (e.g.,hydraulic and/or pneumatic piston-cylinder assembly), a swing linkassembly 16, a packer wheel assembly 18 (e.g., packer arm), and a packerwheel 20. Precision hoe opener assembly 10 may be towed, pushed, orgenerally moved by a vehicle, such as a tractor (not shown). Forexample, the frame support 12 may interface tool frame tow bar 22attached to the tractor for towing the precision hoe opener assembly 10.The precision hoe opener assembly 10 is mounted to the tractor supportvia mounting brackets 24. In the present context, the precision hoeopener assembly 10 may also be generally referred to as an openerassembly, a hoe opener, a row unit, a seeder, a planter, an opener or aground engaging tool/assembly. Further, the ground engaging tool oropener is the portion of the hoe opener assembly that contacts theground, thereby preparing the soil for seed deposition.

Tool frame support 12 is connected to the swing assembly 16 and packerwheel assembly 18 via the cylinder 14, first member 26, and secondmember 28. The mounting configuration of cylinder 14, first member 26,and second member 28 will be discussed further below. Elements 12, 26,28 and 58 collectively form a hydraulically driven parallel linkageassembly. As depicted, cylinder 14 is drives the parallel linkageassembly. Cylinder 14 is mounted to swing link assembly 16 via pin 30.Cylinder 14 is hydraulically coupled to a power supply 32 that may beused to pressurize piston rod 34 to actuate the swing link assembly 16.Once actuated, swing link assembly 16 may engage packer wheel assembly18 via a stop as will be described further below.

The swing link assembly 16 engages the packer wheel assembly 18 via ashank mount adapter 36. The shank mount adapter 36 is coupled to shank38 and first opener 40. Shank mount adapter 36 may be coupled to shank38 via fasteners 42, which allow height adjustments for opener 40relative to opener assembly 10 and optional second opener 50. Packerwheel assembly adjustments may be made via adjuster 44. First opener 40is coupled to a seed distribution header 46 via a seeding tube 48 toallow product deposition during operation. As depicted, a seed is theproduct being deposited in the terrain. The present embodimentillustrates an optional second opener 50, which may be added in somecases to allow for a second product to be placed in the ground. Theadjustments enabled by fasteners 42 and adjuster 44 may optimize productplacement accuracy by allowing packer wheel 20 to move vertically withrespect to first opener 40 and second opener 50. Moreover, the optionalsecond ground engaging tool may affect the packing forces and/orcompensation of the system, but would likely not significantly affectthe basic design of the precision hoe opener assembly and swing linkmechanism.

The diagram also shows first member 26 attached via pins 54 and 56 totool frame support 12, rear frame 58, and packer wheel assembly 18.Second member 28 is also connected to rear frame 58 and tool framesupport 12 via pins 60 and 52. Further, pins 60 and 54 couple rear frame58 to the packer wheel assembly 18 and shank mount adapter 36 as well asto second member 28. The members 26 and 28 with frame support 12 andrear frame 58 form a second parallel linkage assembly.

As discussed above, cylinder 14 actuates swing link assembly 16 to loadshank 38, which further loads packer wheel assembly 18 and packer wheel20. In certain embodiments, the packer wheel 20 provides a substantiallyconstant force to the soil after the seed product has been deposited.Packer wheel 20 is coupled to packer wheel assembly 18 via a rotatingbearing assembly. Further, packer wheel assembly 18 includes multiplemounting locations on adjuster 44 to allow for a positional adjustmentof the packer wheel 20. As stated above, seeding accuracy may beenhanced by adjusting the position of packer wheel 20.

FIG. 2 illustrates a side view of an embodiment of the precision hoeopener 10. The figure illustrates the precision hoe opener 10 in thedeployed position with first opener 40 in an elevated position ascompared to packer wheel 20. In the illustrated embodiment, cylinder 14causes swing link assembly 16 to rotate about pin 60 and to engage shankmount adapter 36, while a obstacle may cause first opener 40 to beraised above the plane of packer wheel 20 and second opener 50.

FIG. 3 illustrates a portion of the precision hoe opener 10 with certainfeatures removed for clarity, such as packer wheel 20, packer wheelassembly 18, and first member 26. The figure illustrates the tool framesupport 12, cylinder 14, second member 28, swing link assembly 16, andshank mount adapter 36. Further, FIG. 4 is a perspective view of theshank mount adapter 36, swing link assembly 16, and their relatedelements.

Referring to both FIGS. 3 and 4, shank mount adapter 36 includes a mainbody having a number of features. These features interface the swinglink assembly 16 to the shank mount adapter 36 during either retractionor extension of the cylinder 14. The swing link assembly includesextension mating feature 62 that interfaces with extension contactsurface 64 as well as retraction feature 66 and surface 68. Thesefeatures provide greater leverage about pin 60 for cylinder 14, reducingthe amount of hydraulic power needed to move the opener assembly. Hole70 provides a mounting location for the end of piston rod 34 in theswing link assembly. Pin 72 is provided for the opposite end of thecylinder 14 to mount to tool frame support 12. The swing link assembly16 may be described as contacting the surfaces of shank mount adapter 36at the extremities of the angular rotational movement of the swing linkassembly 16.

As will be appreciated by one skilled in the art, a portion of theangular movement of the swing link assembly 16 will not cause movementof shank adapter 36 and first opener 40. This characteristic may causethe swing link assembly 16 to be referred to a lost motion linkage.

FIG. 4 shows the swing link assembly 16 in the extended position toengage the shank mount adapter 36, extending the first opener 40 andpacker wheel assembly 18 generally downward. In this position, extensionmating feature 62 engages extension contact surface 64. In the presentembodiment, the geometry of swing link assembly 16 reduces the requiredlength for members 26 and 28 necessary to raise and lower openerassembly 10.

Referring back to FIG. 3, the swing link assembly 16 is shown in theretracted or transport position, e.g., the first opener 40 is liftedhigher than the packer wheel 20. In the illustrated retracted position,retraction mating feature 66 engages retraction contact surface 68. Asshown in both FIGS. 3 and 4, the cylinder 14 and piston rod 34 are notdirectly coupled to shank mount adapter 36. Instead, the first opener 40is retracted and extended via the swing link assembly 16 engaging anddisengaging the shank mount adapter 36.

FIG. 5 illustrates an embodiment of the precision hoe opener 10 in aneutral position as might be representative of being towed during aseeding operation on level ground. In this deployed position for theseeder, shank mount adapter 36 rotates about pin 60 to lower firstopener 40 and engage frame stop 74 located on rear frame 58. When shankmount adapter 36 rotates about pin 60 and a cavity located on theadapter engages the top surface of the frame stop 74, shank mountadapter 36 loads packer wheel assembly 18 which is coupled to rear frame58. The resulting force applies a load to packer wheel 20 via themultiple linkage assembly. Further, when in the extension position, asshown in FIG. 4, frame stop cavity rotates as well, engaging frame stop74, to provide a lowering force upon the packer wheel assembly. Itfollows, that when the swing link assembly 16 is in a retractionposition, as shown in FIG. 3, the frame stop 74 may provide a liftingforce to the packer wheel assembly with contact on the bottom face.

Further, tool frame support 12 is a distance 76 from terrain 78. Duringnormal operation, first opener 40 may plow through terrain 78 creating adraft force 80 on first opener 40. In this position, cylinder load 82 isdirected along cylinder axis 84. Linkage axis 86 runs through the centerof parallel linkage member 28. Reference numeral 88 represents the smallangle between cylinder axis 84 and linkage axis 86. The normal load onpacker wheel 20, generally represented by numeral 90, may mainly consistof the weight of opener 10 with a nominal contribution by cylinder load82. Hydraulic cylinder 14 serves primarily to keep first opener 40 in adeployed position and is connected to the assembly by pins 72 and 30.

FIG. 6 illustrates an embodiment of the precision hoe opener 10 in asecond deployed position. In this position, the relative distancebetween tool frame support 12 and terrain 78 has decreased from that ofFIG. 5 and is represented by numeral 94. This decrease in the distancetypically occurs during terrain changes. The terrain provides draftforce 80 on first opener 40, thereby increasing the packing force 90 ofthe packer wheel 20 on the terrain 78 due to the orientation of thelinks 26 and 28 relative to the direction of the application of thedraft force. In the illustrated embodiment, cylinder 14 may provide alifting force to counteract the increased packing force 90 on the packerwheel 20 due to a decrease in angle 88. Cylinder load 82 produces aresultant force in the opposite direction of packing force 90, therebycompensating for a portion of the downward force created by the draftforce 80 on first opener 40.

FIG. 7 illustrates an embodiment of the precision hoe opener 10 in athird deployed position. In this illustration, relative distance 96between tool frame support 12 and terrain 78 has increased relative toFIGS. 5 and 6. As discussed above, this increase may be dependent on theterrain in the field. In this illustration, the relative increase in thedistance between tow bar 22 and terrain 78 causes draft force 80 toreduce the packer force 90 on the packer wheel 20 due to the orientationof links 26 and 28 relative to the direction of the draft force 80. Theupward resultant force on the opener assembly 10 decreases the packingforce 90 exerted on terrain 78. Optimally, it is desirable to maintain aconstant packing force 90 by the packer wheel 20 on the terrain 78 toensure accurate and consistent seeding. As illustrated by the figure,when the relative distance increases, the piston load 82 may act alongcylinder axis 84 and the relative angle 88 increases which in turnincreases the contribution of the piston load to the packing force 90,on the packer wheel 20. In other words, the cylinder 14 compensates forthe decrease in packing force created by draft force 80.

In general, FIGS. 5, 6, and 7 illustrate that the precision openerassembly 10 has an increased range of motion while providing a generallyconstant packing force to the soil. This is achieved in part by theopener assembly 10 maintaining a substantially constant angle betweenpacker wheel assembly 18 and terrain 78, as well as the geometry ofcylinder 14, first member 26, and second member 28.

As appreciated by one in the art, the disclosed embodiments of precisionopener 10 provide control of the packing force 90 and the seeding depthof the first opener 40. The opener 10 advantageously responds tovariations in the terrain 78, the draft force 80 on the first opener 40,the packing force 90, or a combination thereof. Thus, the opener 10 canprovide a generally uniform packing force 90 and seeding depth toimprove the overall quality of the seeding process, and in turn improvesubsequent growth originating from the seeds. Again, the hoe opener 10has a variety of adjustment mechanisms to control the location of thepacker wheel 20, the first opener 40, the optional second opener 50, ora combination thereof.

FIG. 8 illustrates the implement assembly, including precision openerassemblies 10, as row units of a complete agricultural seeding system98, as may be towed behind a tractor (not shown).

FIG. 9 illustrates an embodiment of precision hoe opener 110 featuring asingle ground penetrating tool 40, shank 38, and shank mount adapter 36.Precision hoe opener assembly 110 includes a tool frame support 12,which may interface with a tow bar (not pictured) located on animplement assembly. The precision hoe opener assembly 110 may be mountedto the tow bar via mounting brackets 24.

Tool frame support 12 is connected to swing link assembly 16 and rearframe 58 via an actuator, in the form of hydraulic cylinder 14, and aparallel linkage arrangement formed by first member 26, and secondmember 28. Cylinder 14 is hydraulically coupled to a power supply (notpictured) that may be used to actuate the swing link assembly 16. Onceactuated, swing link assembly 16 may engage packer wheel assembly 18 viastop 74 contacting shank mount adapter 36. The shank mount adapter 36 isrigidly coupled to shank 38 and ground engaging tool 40. This embodimentmay also feature a seeding and/or fertilizing apparatus (not pictured)behind tool 40 to deposit seeds, fertilizer, and so forth into theopened soil. The arrangement may optimize seeding accuracy by adjustingthe position of packer wheel 20 relative to ground engaging tool 40.Further, the arrangement allows packer wheel 20 to provide asubstantially constant force to the soil after the seed and/orfertilizer have been deposited.

In the illustrated embodiment, first member 26 attached via pins to toolframe support 12, and rear frame 58. Second member 28 may also beconnected to rear frame 58 and tool frame support 12 via pins. Members26 and 28, with frame support 12 and rear frame 58, form the parallellinkage assembly that maintains the orientation of the packer wheelassembly 18 with respect to the ground. The parallel linkage may be usedto control the forces on ground engaging tool 40 and packer wheel 20 asthe precision hoe opener 110 is towed across the terrain. In theillustrated embodiment, the arrangement allows cylinder 14 to actuateswing link assembly 16, loading shank adapter 36 and ground engagingtool 40, which further loads packer wheel assembly 18 and packer wheel20.

FIG. 10 is a side view of the same embodiment of the precision hoeopener 110 featuring a single ground penetrating tool 40, shank 38, andshank mount adapter 36. This figure illustrates the precision hoe opener110 in the deployed position with ground engaging tool 40 in a positionto open the soil, and with packer wheel 20 positioned to pack theopened, seeded terrain. In the illustrated embodiment, cylinder 14causes swing link assembly 16 to rotate about pin 60 and to engage shankmount adapter 36, and ultimately, once the adapter is sufficientlyrotated, rear frame stop 74. When shank mount adapter 36 engages rearframe stop 74, cylinder 14 may exert force on the tool and wheelcomponents through the intermediary of the swing link assembly 16.

FIG. 11 illustrates an exploded view of this embodiment of the precisionhoe opener 110 featuring a single ground penetrating tool 40, shank 38,and shank mount adapter 36. As illustrated, the various components maybe made as weldments, as in the case of the presently contemplatedconfiguration of tool frame support 12, rear frame 58 and packer wheelassembly 12, or as castings, as illustrated for swing link assembly 16,member 28 and shank mount adapter 36. Other manufacturing processes andphysical configurations may, of course, be envisaged for these oranalogous parts. The single ground penetrating tool 40 is bolted to theshank mount adapter 36 in the illustrated embodiment. In the finalassembly, one or more conduits may be provided on the single groundpenetrating tool to channel seeds, fertilizer and the like to theopening formed by the tool as the implement is advanced across terrainto be seeded.

While only certain features of the invention have been illustrated anddescribed herein, many modifications and changes will occur to thoseskilled in the art. It is, therefore, to be understood that the appendedclaims are intended to cover all such modifications and changes as fallwithin the true spirit of the invention.

1. A method of manufacturing an agricultural system, the methodcomprising: mounting a ground engaging assembly to extend from a supportstructure; mounting a second ground engaging assembly to extend from thesupport structure and positioned aft of the first ground engagingassembly along a direction of travel; and mounting a lost motion linkageon the support structure, the lost motion linkage being configured tocooperatively contact the support structure to raise the ground engagingassembly after movement of the lost motion linkage through an angularrange; wherein the support structure includes a shank adapter, the firstground engaging assembly being rigidly mounted to the shank adapter, thelost motion linkage is pivotally mounted to the shank adapter, and thelost motion linkage contacts the shank adapter at two extremities of theangular range.
 2. The method of claim 1, comprising mounting a packerwheel assembly extending from the support structure aft of the groundengaging assembly, the packer wheel assembly being raised by contactwith the shank adapter.
 3. The method of claim 1, comprising coupling alinear actuator coupled to the support structure and to the lost motionlinkage, wherein the linear actuator is configured to raise and lowerthe ground engaging assembly by pivotal movement of the lost motionlinkage.
 4. The method of claim 1, wherein the support structureincludes a parallel linkage for raising and lowering the ground engagingassembly.